Machine



'(No Model.) 6 Sheets-Sheet 1.

H. O. WARREN. MACHINE FOR GENERATING GEAR TEETH. No. 559,011. PatentedApr. 28, 1896.

T'Vitnesses: jnz'enior .Hmlarren zijfiil s'flfiarze l (No Model) 6Sheets-Sheet 2.

H. O. WARREN. MACHINE FO GENERATING GEAR TEETH.

No. 559,011. PatentedApr. 28, 1896.

- In men (or Wi Ines ses HCWarren (No Model.) 6 Sheets-Sheet 3.

H. O. WARREN. MACHINE FOR GENERATING GEAR TEETH.

No. 559,011. Patented Apr. 28, 1896.

WVitn esaes (Was 12 (No Model.) 6 Sheets-Sheet L.

H. (3.1 WARREN. MACHINE FOR GENERATING GEAR TEETH. No. 559,011. PatentedApr. 28, 1896..

(No Model.) 6 Sheets-Sheet 5.

H. O. WARREN.

MACHINE FOR GENERATING GEAR TEETH.

No. 559,011. Patented Apr. 28, 1/896.

Willi leases: [74 U8 (or;

V Y T flCWarrei a.

q zz'slzzom (No Model.) 6 Sheets-Sheet 6.

H. G. WARREN.

MACHINE FOR GENERATING GEAR TEETH.

No. 559,011. Patented Apr. 28, 1896.

i 1 5 1' i W;' in 35 i111: fig; Ly-5:3 Li" 1311113 17136?! B V E CWarren@318 l ltorrfl UNITED STATES HERBERT C. TARREN, OF

PATENT OFFICE.

HARTFORD, CONNECTICUT.

MACHINE FOR GENERATING GEAR-TEETH.

SPECIFICATION forming part of Letters Patent No. 559,01 1, dated April538, 1896. Application med November 5,1895. Serial No. 567,982.tNomodel.)

To all whom it may concern.-

Be it known that I, HERBERT QWARREN, a citizen of the United States,residing at Hartford, in the county of Hartford and State ofConnecticut, have invented certain new and useful Improvements inMachines for Generating Gear-Teeth, of which the following is aspecification.

My invention appertains to machines for generating gear-teeth, and itrelates more particularly to that class of machines especially designedforcutting the teeth of spur-wheels.

One object of my present invention is to furnish a machine of the classspecified of improved and simplified construction and organization andwhich is especially adapted for generating the teeth of spur-wheels withrapidity, precision, and economy.

' An other object of my inventionis to furnish an improvedgear-tooth-generating machine comprehending a reversibly-revolublegearblank carrier and a continuouslyrotative andlongitudinally-reciprocative cylindrical or polygonal tooth-cutting.rack or multiplex cutter, and to provide, in operative connection withthe gear-blank carrier and toothcutting rack, actuating mechanism inposition and adapted for continuously rotating the cutting-rack, and atthe same time imparting a rotary movement to the gear-blank carried bythe carrier and a longitudinal movement to the cutting-racksimultaneously in coinciding directions and at the same peripheralvelocities, and also adapted for simultaneously reversing the directionof movement of the gear blank and cutting rack at predetermined pointsin the movement of the cuttingrack, and also for changing the relativetrans verse positions of the gear-blank and cuttingrack at predeterminedpoints in the movement of said cutting-rack, whereby the operation ofthe cutting of the teeth in the gearblank will be continuous, andwhereby the cutting-rack will act upon the entire circuit of thetooth-forming portion of the gear-blank at every complete stroke of saidrack.

Another object of my present invention is to provide, in cooperativerelation with a 0011- tinuously-rotative gear-blank carrier, in amachine of the class specified, an elongated multiplex cutter of alength not less than the peripheral length of the gear-blank carriedtudinal axis substantially at right angles to the axis of the gear-blankcarrier and adapted for rotation and for longitudinal reciprocation, andmeans for continuously rotating the cutter and for simultaneouslyimpartinga rotary movement to the gear-blank and a longitudinal movementto the cutter in the same direction and at corresponding peripheralvelocities and for effecting one complete rotation of the gear-blankcarrier to every complete stroke of the cutter, as will be hereinaftermore fully described.

In the accompanying drawings, forming a part of this specification,Figure 1 is a plan view of a gear-tooth-generating machine embodying mypresent invention, portions thereof being broken away to more clearlyillustrate the construction and organization of certain of the details,the tooth-generating rack or elongated cylindrical cutter being shown inits extreme retracted positionthe position it occupies during its firstoperation in cuttingablank. Fig. 2 is a side elevation of thegear-tooth-generating machine, seen from the under side in Fig. 1, aportion of the bed of the machine being broken ofi and the gear-blankand cutter being shown in the same position illustrated in Fig. 1. Fig.3 is a side elevation of the gear-generating machine, seen from theopposite side to that shown in Fig. 2, the gear-tooth-generating rackbeing shown in this figure near the end of the forward movement. Fig. 4is an end elevation of the gear-generating machine, seen from the lefthand in Fig. 1. Fig. 5 is a vertical sectional view of the machine,taken in dotted lines a a, Fig. 2, looking toward the right hand in Fig.3. Fig. 6 is a plan view of a portion of one end of the machine,partially in section, and showing the general construction andorganization of the reversing driving mechanism and subsidiary elements.Fig. 7 is a side elevation of the mechanism shown in Fig. 6, seen fromthe under side in said figure, a portion of the framework being shown indotted lines. Fig. Sis an end view of a portion of the mechanism whichactuates the belt-shipper cam, seen from the right hand in Fig. 7, aportion of the framework being shown in dotted lines. Fig. 9 is asectional end view of a portion of the gear-toothby the carrier, andsupported with its longi- 4 generating machine, showing aslightly-modified form of synchronizing actuating mechanism between thegear-blank carrier and cuttor-carrier.

By the term multiplex cutter, as herein applied, is meant a rotativeelongated racklike cutter, of cylindrical or polygonal crosssection,comprehending a multiplicity of circumferentially-disposedtooth-cutters, each of a cross-sectional shape-in the the plane of itsaxis of rotation-similar to a truncated Wedge, and which cutters areseparated from shape suitable for each other by adistance substantiallyequal to the width of the teeth it is desired to generate. Thistooth-cutter may in practice consist of a toothed ring, disk, or flange,of a generating the required form of gear tooth.

To generate the teeth of spur-gears in accordance with my presentinvention, it is desirable that the gear-blank shall have a continuousuninterrupted rotative movement for a distance not less than theperipheral length of said blank, and that a multiplex cutter,comprehending a multiplicity of continuously-rotative cutters, be movedinto contact and along with the gear-blank in the same direction anduninterruptedly for a distance equal to the peripheral length of thegearblauk and with the same peripheral velocity, to thereby generate aportion of each tooth of the entire circuit of teeth at one cuttingoperation; and it is further desirable that the direction of movement ofthe gear-blank and multiplex cutter be reversed at the end of each andevery complete rotation of the gear:

blank, and that the multiplex cutter shall be operable for performingits cutting function in both directions of its reciprocatory movement,which may be accomplished by changing the relative transverse positionsof the gearblank and cutter at predetermined points in the length of theworking stroke of the cutter.

As an instrumental-ity for generating the teeth of spur-gears inaccordance with my present invention 1 have shown in the drawings atheoretical adaptation of mechanism for supporting the gear-blank andmultiplex cutter in proper cooperative relation and for automaticallyeffecting the requisite movements of the gear-blank and cutter, to formin said gear-blank theoretically-correct gearteeth by progressiveand-uninterrupted backward and forward cutting operations of saidcutter.

In the preferred organization thereof herein shown and described myimproved machine for generating gear-teeth comprehends, in part, acontinuo-usly-rotative gear-blank carrier, (designated in a general wayby 0,)which is supported for movement transversely of the axis of arotative tooth-generating-cutter, and

which is also supported for adjustment in a ment in a plane parallel toa line tangent to the periphery of a gear-blank, as G, carried by thegear-blank carrier, a multiplex toothgenerating cutter (designated in ageneral way by 0 supported for rotation about an axis substantially atright angles to the axis of the gear-blank carrier, and comprehending aseries of peripherally-disposed tooth-cutters separated transversely, orin the plane of their axes, by intervening tooth-formative spaces,actuating mechanism forthe gear-blank carrier, cutter, andcutter-carrier, comprehending means for continuously rotating themultiplex cutter, also for simultaneously imparting a rotative movementto the gear-blank and a longitudinal movement to the cutterin coincidingdirections and with corresponding peripheral velocities, also foreffecting one complete rotation of the gear-blank carrierto everycomplete stroke of the cutter, and also for simultaneously reversing thedirection of movements of the gear-blank and the cutter and feedmechanism controlled by the movements of the cutter-carrier, and forautomatically effecting a change in the relative transverse positions ofthe gear-blank and cutter, all of which will be hereinafter more fullydescribed.

The framework of my improved gear-toothgeneratin'g machine, whichframework may be "of any suitable general construction for carrying theoperative parts, consists, in the preferred form thereof herein shown,of a main frame, (designated in a general way by F,) which framesupports the cutter-carrier and certain elements of its subsidiarymechanism, and an overhanging auxiliary frame, (designated in a generalway by F,) which is supported for vertical adjustment on themain frameand supports the gear-blank-carrier and certain elements of itssubsidiary mechanism.

The main frame F, or cutter carrier frame, as it may be hereinaftertermed, is shown in the drawings somewhat similar to an ordinaryplaner-frame, it consisting of the base B, having the usual longitudinalguideway 2 midway of its width, and having the uprights B and B locatedat opposite sides of the bed and approximately midway between theopposite ends of said bed, which uprights B and B have verticalslideways 3 and 4 thereon to receive the slides 5 and6 on thesupplemental frame F, or gear-blank-carrier frame, as it may behereinafter termed.

The blank-carrier frame F, which is shown as a U-shaped frameoverrea-ching the base of the machine, has slides 5 and 6, preferablyformed integral with the ends thereof. These slides are carried forvertical adjustment on too the slideways 3 and 4, respectively, on theuprights B and B and are shown in the nature of sliding brackets havinghorizontal bearings 7 and 8, formed, respectively, there: in, the axesof which bearings are coincident and are transversely disposedrelatively to the longitudinal axis of the base B of the machine, aswill be understood by reference to Figs. 1 to 5, inclusive, of thedrawings. These bearings are intended to receive the rotative gear-blankcarrier, (designated in a general way by 0,) the construction andorganization of which gear-blank carrier will be hereinrier-adj ustingmechanism, which, in the form thereof herein shown, consists of two adjusting-screws 9 and 10, journaled in bearings at their upper ends 12 and13 at opposite sides of the frame F, and having screw-threaded bearingsat their lower ends in the upper ends of the uprights B and 13respectively, said adjusting-screws 9 and 10 being shown provided attheir upper ends with bevel-gears 9 and 10', respectively, which meshwith similar bevel-gears 14 and 15 at opposite ends of a screw-actuatingshaft 16, jonrnaled in horizontal bearings 17 and 18 upon the upper endof the blank-carrier frame at opposite sides thereof. This shaft 16 hasa cross-seetionally angular end 16, extended beyond the intermeshinggears and adapted to receive a crank or other suitable tool, by means ofwhich this shaft and .the connected adjusting screws may be rotated toraise orlower the blankcarrier frame, as will be understood by referenceto Figs. 1 to 5, inclusive, of the drawmgs.

The cutter carrier .0 (shown somewhat similar, in a general way, to anordinary planer-bed) is supported for reeiprocatory movement on theguideway 2, and is shown having at opposite ends thereof bearings 19 and19 to receive the ends of the multiplex tooth-generating cutter 0 theextended core or shaft of which is journaled at opposite ends forrotation in said bearings.

In the preferred form thereof .shown in the drawings the multiplextooth-generating eutter 0 comprises a multiplicity oftransverselyequidistant tooth-milling cutters 21, detachably fixed to ashaft 20, which, as before stated, is journaled at opposite ends thereoffor rotation in the bearings 19 and 19 of the cutter-carrier O.

,It is desired to state in the above connection that while it ispreferable to employ a multiplicity of independent milling-cutters andto practically secure them upon a shaft, as 20, extending centrally theentire series of cutters, this construction and arrangement might bemodified somewhat without departure from myinvention. For conveniencethe shaft 20 and the milling-cutters 21 thereon, irrespective of thefact that the cutters may be separate from or form an integral part of Ithe shaft 20, will be hereinafter referred to as the multiplex cutter,said multiplex cutter being somewhat in the nature of a rotativecylindrical rack, the teeth of which have cuttingfaecs of a shapeadapted for generating a tooth-space in a gear-blank.

In practice the multiplex tooth-generating cutter C will have itscutting-faces of an aggregate length, longitudinallyof the axis thereof,not less than the peripheral length of the gear-blank to be operatedupon, and it will be adapted for generating-a portionof each tooth ofthe entire circuit of teeth to be generated in the gear-blank at eachcomplete forward and backward movement of said mul tiplex cutter.

As a means for continuously rotating the multiplex tooth-generatingcutter duringaud throughout the reeiprocatory movements of said cutter Ihave shown the .phaft or core 530 of said cutter furnished with aspur-wheel 22, V

which is geared with a pinion 24 through the medium of the intermediateidle-wheel 23,

and this pinion 24 has a hub 24', journaledin a bearing 25 upon anoutwardly-extending arm or bracket 26 on the cutter-carrier C, and isheld in place so as to move with the cutter carrier and bracket,preferably by means of an internally-screw-threaded collar 27, screwedonto the end of said hub, as shown most clearly in Fig. 2 of thedrawings. This pinion 24 is splined upon and is adapted to be movedlongitudinally of a cutter-rotating driven shaft 28, which is supportedat opposite ends in bearings 29 and29' upon the side of a cutter-carrierframe F of the machine,

said shaft 28 being continuously driven in one direction through themedium of suitable driving mechanism (designated in a general I C L.

way by D) and in a manner hereinafter more upon the side of said frame,and which shaft is rotated, first in one direction and then in anopposite direction, to advance and retract the cutter-carrier by meansof the driving mechanism D, which also actuates the cutterrotatingshaft, which driving mechanism is herein shown in the nature ofreversing driving mechanism, and will be hereinafter more fullydescribed.

The gear-blank carrier 0, in the preferred construction and organizationherein shown and described, eomprehends, in part, two axially coincidentlongitudinally separable members 36 and 37, adj ustably connectedtogether, as hereinafter more fully described, for movement together inthe plane of their longitudinal axes and transversely of the multiplexcutter 0 These members are shown conically recessed, as at 38 and 38, attheir inner adjacent ends, to receive the conical ends 39 of an arbor40, which supports the gear-blank G, said arbor practically constitutinga connector between the two carrier members 36 and 37, and being held inplace by means of clamp-rods 41 and 42, which extend through axial boresin the two members 36 and 37, respectively, of the carriers. These rodsare in the nature of elongated bolts having screw-threaded bearings attheir inner ends in the opposite ends of the arbor, and having the heads41 and 42 thereof in bearing engagement with the outer ends of therotative carrier members 36 and 37, respectively.

One of the carrier members, as 36, is shown journaled for rotation in arack-like sleeve 43, supported for reciprocatory movement in ahorizontal bearing, as 7, at the lower end of'the blankcarrier frame F,whereas the other carrier member, as 37, is shown splined forlongitudinal movement in a rotative sleeve 44, journaled in a horizontalbearing, as 8, j

located at the lower end of the blank-carrier frame, F, in axialalinement with the bearing I This last-mentioned sleeve 44 is heldagainst reciprocatory move-' 'ment in the bearing by suitable flanges atthe ends thereof, as shown in the drawings.

7 before referred to.

"Forthepurpose of rotating the gear-blank carrier in synchronism withthe 'reciprocatory movement of the multiplex cutter said gearblankcarrier will. be actuated directly from and controlled in its movementsby the cuttor-carrier, and as a means for efiecting the requisitesynchronous movements of the gearblank carrier and cutter-carrier saidgearblank carrier is shown operatively connected with the cutter-carrierby means of synchronizing actuating mechanism, (designated in a generalWay by S.) This synchronizing actuating mechanism S, which practicallyconstitutes an actuating -connector between the gear-blank carrier 0 andcutter-carrier C, may, in the simplified form thereof shown in Fig. 9,consist of arack 45, fixed to the upper face and extendinglongitudinally of the outter-carrier at one side the axis thereof, and aspur-wheel 46, removably fixed to a rotative member of the sleeve 44 ofthe gearblank carrier and meshing with the rack 45 of thecutter-carrier. In this form of synchronizing mechanism the spur-wheel46,

- which practically constitutes a pattern-wheel for securing, inconnection with the rack 45, the requisite ratio of movement between thegear-blank carrier and the cutter-carrier, will in practice be of thesame diameter and have the same number and form of teeth as thegear-wheel having its teeth generated.

In the form thereof shown in Figs. 1 to 5, inclusive, the synchronizingactuating mechanism between the gear-blank carrier and cutter-carrier isof more complex character, the rack 45 on the cutter-carrier and thespurwheel on the gear-blank carrier being shown,

in this instance, separated and operatively connected together by meansof suitable intermediate gearing (herein shown as a pinion 48) carriedat the inner end of the driven shaft 49 and meshing with the rack 45,this shaft 49 being journaled in suitable bearings with the main frameand carrying a pinion 50 at the outer end thereof, which meshes with anidle-wheel 51 of relatively large diameter, mounted on a stud 52,adjustably fixed to an arm 53, which in turn is shiftably supported onthe shaft 49 and is adapted for adjustment in a plane concentric to theaxis of said shaft, an idle-wheel 54, of relatively small diameter, alsobeing carried on the stud 52 and meshing with the spur-wheel 46.

In the organization of synchronizing actuating mechanism described inthe last preceding paragraph it is necessary to substitute differentsizes of idlewheels 51 and 54 when it is desired to adapt the machinefor cutting and generating gear teeth and blanks of d-ifierentdiameters, so as to maintain the requisite ratio of velocity between thegear-blank carrier and cutter-carrier, Whereas with the modified form ofsynchronizing actuating mechanism shown in Fig. 9 it is necessary toapply a different rack 45 and a dififerent spur-wheel 46 for everydiffercut-sized gear-blank to be cut.

{is a means for adjusting the arm 53, which carries the idle-wheels 51and 54, so as to permit larger or smaller idle-wheels to be placed inoperative relation with the spur-wheel 46 and the pinion 50, said arm 53has a slot 53 at one end thereof, which is concentric to the axis of amovement of said bracket, through which slot is extended a clamping-bolt53", which has a screw-threaded bearing in a fixwill be readilyunderstood by reference to Figs. 2, and 5 of the drawings, and as ameans for facilitating the adjustment of the idlewheels longitudinallyof the arm 53 said arm has a longitudinal slot 55, through which thestud 52, on which the idle-wheels are mounted, is extended, said studbeing screw-threaded at one end and furnished with a nut, by means ofwhich said stud is held adjusted in position on the arm 53.

In the drawings (see Figs. 1, 2, 4, 5, and 9) I have shown two separategear-blanks G G, carried upon the arbor 40 in position to be operatedupon by the multiplex cutter C and as a means for tightly clamping saidblanks in position upon the arbor 40 said arbor is shown peripherallyflanged, as at 40', at one end to form an abutment for the outer face ofthe hub of one of the gear-blanks, and is externally screw-threaded atthe opposite end to receive the clamp-nut 40, which bears against theouter face of the hubs of the other of said gear-blanks, as shown mostclearly in Figs. 4 and 5.

As a convenient means for automatically feeding the blank or blanks G,together with the blank-carrier (J, transversely of the multiplex cutterO at the requisite point in the advancing or retracting movement of thecutter, the sleeve 7, in which the carrier member 36 is journaled forrotation,is shown furnished with a rack 56 at the lower face thereof andlongitudinally disposed relatively to the axis of said sleeve, whichrack meshes with a pinion 57, fixed to a horizontally-disposed shaftjournaled in suitable bearings in a bracket on the blank-carrier frameF, said shaft being provided at its outer end with a wormwheel58, whichmeshes with and is actuated by a worm 59, splined for longitudinalmovement on a feed-shaft 60, which is journaled at its lower end in abearing on a bracket 60, constituting a fixture on the cutter-carrierframe F, and is held against longitudinal movement by suitable collars.At the lower end thereof the feed-shaft 60 is provided with a feed-wheel61, (herein shown as a starwheel,) having a series of radially-disposedarms 61, in position to be engaged by abutments on the cutter-carrierduring the forward and backward movements of said cuttencarrier. Thesefeed-shaft-actuatin g abutments or stops (designated by 62 and 63,respectively) are adj ustably secured to the side of the cutter-carrier,preferably in the manner shown in Figs. 3 to 5, inclusive, and at adistance apart substantially equal to the length of the requisiteeffective stroke of the cutter-carrier. ()ne of saidfeed-Wheel-actuating abutments or stops, as 62, is shown located nearthe rear end of the cutter-carrier, and is adapted for engaging and forpartially rotating the feed-Wheel near the end of the advancingmovement, or preferably at the end of the effective advancing stroke, ofthe cutter-carrier, to thereby feed the gear-blank inward relatively tothe multiplex cutter and bring another portion of the gear-blank intoposition to be operated upon by the cutter upon the retractive stroke ofsaid cutter, and the other of said abutments or stops, as 63, is locatednear the forward end of said outter-carrier, and is adapted for engagingand for partially rotating the feed-wheel at the end of the retractivemovement of the cuttercarrier to bring another portion of the gearblankinto the position to be operated upon by said cutter during the nextadvancing movement of said cutter, as will be readily understood byreference to Figs. 3 to 5, inclusive, before referred to.

The driving mechanism (designated in a general way by D) for eifectin'ga continuous rotation of the multiplex cutter C in one direction and foreffecting an advancing and retracting movement alternately of thecuttercarrier 0 simultaneously with the rotation of the cutter C andwithout effecting a change in the direction of said cutter, may consistof any suitable reversing driving mechanism in operative connection withthe cutter-rotatin g shaft 28, which controls the rotation of thecutter, and with the worm or driving shaft 35, which controls thereciprocation of the cutter-carrier, and which mechanism comprehendsmeans for continuously rotating the V cutter actuating and controllingshaft 28 in 65 on the worm-shaft 35, two loose pulleys 66 and 67, oneat-each side of said fast pulley and two driving-belts, a straight beltand a twist-belt 68 and 69, respectively, (shown in dotted lines inFigs. 2 and 4,) which may lead to the usual driving-pulley on the mainshaft, (not shown,) and which belts are adapted for rotating the fastpulley 65 alternately in opposite directions when said belts are shiftedalternately on and off said fast pulley 65,which may be automaticallyeffected by means controlled by the movement of the cutter-carrier, aswill be hereinafter more fully described.

As a means for. continuously rotating the cutter-actuating shaft 28constantly in one direction and in synchronism with the rotation of thecutter-carrier-actuating shaft 35, irrespective of the direction ofmovement of said shaft 35, the shaft 28 has fixed thereon two pinions 70and 71, located one adjacent to the outer face of each loose pulley 66and 67, as clearly shown in Figs. 1, 2, 6, and 7, and said loose pulleyshave pinions 72 and 7 3,

fixed concentrically thereto, respectively, the

one 72, fixed to the loose pulley 66, being geared to the pinion 70 bymeans of two intermediate idle-wheels 7 0' and 7 2, and the one 73 onthe loose pulley 67 being geared to the pinion 71 by means of oneintermediate idlewheel 71. Thus it will be seen that the loose pulley 66is in geared connection with the cutter-actuating shaft 28 by a train ofgears adapted for rotating said shaft in the same direction that thepulley 66 rotates, whereas the loose pulley 67 is i-n geared connectionwith this shaft 28 by a train of gears adapted for rotating said shaftin a reverse direction from that in which said pulley 67 rotates.Therefore, notwithstanding the fact that the loose pulleys 66 and 67 arerotated by the belts 68 and 69, respectively, alternately in reversedirections, the direction of rotation of the cutter-actuating shaft,which is directly controlled by said loose pulleys, remains unchanged.Normally the belts 68 and 69 are so disposed relatively to each otherand to the three pulleys 65, 66, and 67 that one of said belts extendsover the tight pulley 65 and the other of said belts extends over one orthe other of the loose pulleys 66 and 67, and as a means forautomatically shifting said belts 68 and 69 together or separately, asrequired for reversing the direct-ion of rotation of thecutter-carrier-actuating shaft, or for stopping the rotation of saidshaft, I have provided a beltshifting mechanism, which, in the preferredform thereof herein shown, comprises suitable shipper-levers 75 and 76,

which engage the belts 68 and 69, respectively, and are carried at theirlower ends upon rock-shafts 10 and 76, journaled in o I Q ataoiisuitable bearings transversely of the main frame of the machine, andhaving cranks 7 5" and 7 6" at the opposite ends thereof withprojections engaging' in cam-slots 77 and 7 8', formed in shipper-cams77 and 78, which are supported for sliding movement in a suitableslideway 79 on the side of the main frame F of the machine.

The instrumentality preferably employed for operating the shipper-cams77 and 78 is shown consisting of an actuating-rod 80, journaled forsliding and rotative movements 1n suitable bearings in the frame F inparal-' lelism with the path of longitudinal movement of thecutter-carrier, said actuating-rod being provided with two transversecam-actuating arms 81 and 82, one adjacent to each end of the two cams,and one of said arms being. adapted, when in the position shown ,inFigs. 4 and 5 of the drawings, for engaging ably, at or near the extremeends of the longi- 68 and 69 alternately onto the tight pulley 65,

; effecting a change in the direction of rotation and therebyalternately rotate the carrieractuating shaft 35 in opposite directions,and effect an automatic reversal in the direction of movement of thecutter-carrier, Without of the multiplex cutter O As it is sometimesdesirable to stop the longitudinal movement of the cutter-carrier, aswhen the generation of the teeth in. the gearblank has been completed, Ihave provided, in connection with the shipper-cam-actuating rod, anautomatic stopping device controlled by the movement of the gear-blankcarrier C transversely of the cutter C This means, in the form thereofherein shown, consists of a rock-shaft 86, having a sliding fit in ajournal 86 on the blank-carrier frame F and havingits lower endjournaled in a bearin g on the cutter-carrier frame F, as shown mostclearly in Figs. 3, 4, and 5, and an actuating-arm 87,'splined to theshaft 86 between abutments on the frame F and having its outer free endlocated in the path of movement of a projection 88 on the gear-blankcarrier 0. This rock-shaft 86 is operatively connected at its lower endwith 'an arm 89'on the cam-actuating rod by acrank connection,(designated in a general way by H,) which may be of any suitableconstruction for partially rotating the cam-actuating rod upon a partialrotation cam upon the longitudinal movement of the cam-actuating rod 80,as is required for shifting one of the belts, as '68, independently ofthe other belt onto the loose pulley, and thereby stop the rotation ofthe cutter-carrier-actuat-ing shaft 35 immediately upon the operation ofthe automatic stopping device by the gear-blank carrier.

It is desired to state in the above connection that the mechanismemployed for actuating the cutter and cutter-carrier and the mechanismemployed for automatically reversing the direction of movement of thecutter-carrier and for automatically stopping the cutter-carrier may bevariously modified within the scope and limits of my invention, and alsothat the means for efiecting the requisite ratio of movement between thegear-blank carrier and cutter-carrier may be variously modified withoutdeparture from my invention.

The invention is obviously not limited to a cutter-carrier reciprocatingin a right line, but comprehends any movable cutter-carrier capable ofconnection with the gear-blank carrier for the purpose stated.

Having thus described my invention, what I claim isp 1. The combinationof a reversibly-rotative gear-blank carrier; a reciprocativecutter-carrier; and actuating mechanism for synchronously moving thegear-blank carrier and cutter-carrier, first in one and the samedirection, and then in the opposite and the same direction, atcomparative velocities of .a predetermined ratio.

- 2. The combination of a rotatixe gear-blank carrier; actuatingmechanism for rotating'the gear-blank carried by the gear-blank carrier,first in one, and then in the opposite, direction; a rotative,multiplex, tooth-generating cutter in operative relation with thegearblank carrier; means for continuously rotatin g the multiplexcutter; and means for moving. the cutter endwise at substantially thesame speed as the pitch-line of the revolving blank in which the teethare to be cut, and

first in one, and then in the opposite, direc-- the blank to be cut; amovable cutter-carrier;

and means actuated by the cutter-carrier forrotating the blank-carrier.

4. The combination of a rotative gear-blank carrier; a reciproeativecutter-carrier supported in operative relation with the gearblankcarrier; a rotative, multiplex cutter carried by said carrier, andhaving its efiective stroke of a length not less than the peripherallength of the gear-blank in which the teeth are to be generated; andsynchronizing actuating mechanism for rotating the gear-blank carrierand cutter, and for imparting to the cutter an endwise-working stroke ofa length not less than the peripheral length of the gear-blank in whichthe teeth are to be generated, at each complete rotation of thegear-blank carrier, and in the direction of, rotation of the gear-blankcarrier, and at right angles to the axis of said carrier.

5. The combination of a reversibly-rotative gear-blank carrier; areciproeative cuttercarrier; a rotative, multiplex cutter carried bysaid cutter-carrier; actuating mechanism for synchronously rotating thegear-blank carrier, first in one direction and then in the oppositedirection, and for simultaneously rotating the multiplex cutter and atthe same time moving the same longitudinally at a velocity correspondingsubstantially with the pitch-line velocity of the blank in which theteeth are to be generated, and first in one and then in the oppositedirection, coinciding with the directions of movements of theblank-carrier; and means controlled by the movements of thecutter-carrier for automatically ch nging the relative transverserelations of the gear-blank carrier and cuttercarrier.

6. A machine for generating gear-teeth, comprehend in g a multiplexcutter, of a length not less than the peripheral length of thegear-blank in which the teeth are to be generated; a carrier for thegear-blank; actuating mechanism for imparting to the cutter andgear-blank a motion'corresponding to the motion of a rack and anintermeshing, rotating pinion, and for moving said cutter a distance notless than the peripheral length of the gear-blank at each stroke of thecutter and at each complete rotation of the gearblank; means forcontinuously rotating the multiplex cutter; and feeding mechanism forautomatically changing the relative transverse relation of thegear-blank and cutter intermediate to successive cutting strokes of saidcutter.

' 7. In a machine of the class specified, arotative gear-blank carrierand a reciproeative cutter-carrier, supported, one above the other, withtheir axes of movement in planes intersecting each other; in combinationwith means for reciprocating the cutter-carrier; and anactuatii'ig-connector between, and operatively connecting, thegear-blank and cutter-carrier and adapted for rotating the gearblankcarrier in synchronism with the movements of the cutter-carrier, and forestablishing a predetermined ratio of movement between saidcutter-carrier and gear-blank. carrier.

8. A machine for generating gear-teeth, comprehending anaxially-rotative cutter of a length not less than the peripheral lengthof the blank to be cut, a rotative gear-blankcarrying member and areciproeative cuttercarrying member, oneof which carrying members isinoperative connection with, and is directly actuated by, the other inthe same direction and at comparative velocities of a predeterminedratio; and means for actuating one of said members. a

9. A machine for generating gear-teeth, comprehending areversibly-rotative blankcarrying member; a reciproeativecutter-carrying member in direct geared connection with theblank-carryin g member, and havingthe plane of its movements transverseto the axis of rotation of the blank-carrying member and a rotativemultiplex cutter carried by the cutter-carrying member; actuating meansfor reciprocating the cutter-carrying member; and means for rotating thecutter simultaneously with the reciprocatory movement of thecutter-carrying member, substantially as described.

10. In a machine for generating gear-teeth, a rotativegear-blank-carrying member and a reciproeative cutter-carrying member,one of which is in operative connection with, and is directly actuatedby, the other; means for actuating one of said members; and meanscontrolled by one of said members for changing the relative transverserelations of the two members, substantially as described, and for thepurpose set forth.

11. In a machine for generatinggear-teeth,

a rotative carrier for the gear-blank; a cut- 12. In a machine forgenerating gear-teeth,

a rotative gear-blank carrier and a longitudinally-movablecutter-carrier supported with their axes of movement in relativetransverse planes; a rack on the cutter-carrier; a pinion I on thegear-blank carrier in geared connection with the rack on thecutter-carrier; a rotative multiplex cutter carried by the cut-.ter-carrier with its axis of rotation transverse to the axis ofthe'gear-blank carrier; actuatin g mechanism for imparting longitudinalmovements to the cutter -carrier; rotating mechanismin connection withthe cutter; and feeding mechanism for efiecting a change in thetransverse relations of the gear-blank car-- rier and cutter,substantially as described, and for the purpose set forth.

13. In a machine for generating gear-teeth, a rotative gear-blankcarrier; a multiplex cutter supported for rotation in longitudinalmovement below, and with its axis in a plane at right angles to, theaxis of the geanblank; reversing driving mechanism for rotating thecutter continuously in one direction, and for moving the samelongitudinally, first in one, and thenjn the opposite, direction; andactuating mechanism for rotating the gearblank carrier, first in onedirection and then in the opposite direction, in synchronism andcoinciding with the directions of movement of the cutter, to establish auniform peripheral velocity between the cutter and the gearteeth inwhich the teeth are to be generated.

14. In a machine for generating gear-teeth, a rotative gear-blankcarrier; a reciprocat-ive cutter-carrier having its plane of movementtransverse to the axis of the gear-blank carrier and a rotativemultiplex cutter; in combination with reversing driving mechanism inconnection with, and adapted for moving,

the cutter-carrier longitudinally, first in one,

and then in the opposite direction; cutter-rotating mechanism inconnection with, and adapted for continuously rotating, the cutter;gearing intermediate to, and operatively connecting, the reversingdriving mechanism and the cutter-rotating mechanism; synchronizingactuating mechanism intermediate to, and operatively connecting, thegear-blank carrier and cutter-carrier, and adapted for establishing apredetermined ratio of movement between the gear-blank carrier and thecuttercarrier; and feeding mechanism controlled by the longitudinalmovements of the cuttercarrier for effecting a change in the transverserelation of the gear-blank carrier and cutter-carrier, substantially asdescribed, and for the purpose set forth.

15. In a machine of the class specified, the

, combination of a cutter-carrier frame; a cutrotatively and the other.longitudinally in the,

same direction and at comparative velocities of a predetermined ratio.

16. In a machineof the class specified, the combination of acutter-carrier frame; a horizontally-disposed cutter-carrier supportedfor longitudinal movement upon said frame; a multiplex cutter rotativelycarried on the cut ter-carrier'with its axis in the plane of thelongitudinal movement of the cutter-carrier and transversely of agear-blank carrier; a gear-blank-carrier frame supported on thecutter-carrier frame for adjustment vertically thereof; adjusting meansfor said blank-carrier frame; a rotative gear-blank carrier supported onthe blank-carrier frame with its axis transverse of the path of movementof the cutter-carrier, and for adjustment transversely of the multiplexcutter; synchronizing actuating mechanism operatively' connectin g thegear-blank carrier and cutter-carrier, and controlled by the movementsof the cuttercarrier for establishing a predetermined ratio of movementbetween the gearblank carrier and cutter-carrier; actuating mechanism inconnection with, and adapted for moving, the cutter-carrier and thecutter thereon transversely of the plane of the axis of the gear-blankcarrier; rotative mechanism for the cutter; and means controlled by themovement of the cutter-carrier for intermittently feeding the gear-blankcarrier transversely of the cutter.

17. In a machine for generating gear-teeth, a rotative gear-blankcarrier, and a longitudinally-movable multiplex cutter supported withtheir axes in a plane transversely of each other; in combination withactuating mechanism for rotating the cutter, and for simultaneouslymoving the cutter longitudinally, and the gear-blank carrier rotatively,in the same direction at comparative Velocities of a predeterminedratio; reversing mechanism for intermittently reversing together thelongitudinal and rotative directions of movements of the cutter andgearblanl; carrier, respectively; feeding mechanism controlled by thelongitudinal movements of the cutter for automatically andintermittently moving the cutter-carrier transversely of said cutter;and a stopping mechanism controlled by the movement of the cuttercarriertransversely of the cutter for automatically stopping the longitudinalmove- ICC ment of the cutter at a predetermined point cutting length,lon gitudinally of said axis, not

less than the peripheral length of the gearblank in which the teeth are.to be generated; a cutter-carrier; and means connecting said carriers,substantially as described.

19. A rotative multiplex cutter of a length not less than the peripherallength of the blank to be cut, and a movable cutter-carrier in.

x If

combination with a gear-blank carrier; and mechanism connecting saidcarriers.

20. A rotative multiplex cutter of a length not less than the peripherallength of the blank to be cut, and a movable cutter-carrier incombination with a gear-blank carrier; mechanism connecting saidcarriers; and

means for moving one of said carriers transversely.

21. An axially-rotative cutter of a length not less than the peripherallength'of the blank the two carriers and by which one carrier isactuated by the other carrier.

23. A reciprocative carrier, and an axiallyrotative cutter-journaledthereon; in combination with a gear-blank carrier an actuator connectingsaid carriers; means for moving one carrier beneath the other carrier;and means for reversing the direction of movement of one of saidcarriers.

24. A movable carrier and a multiplex cut-. ter of a length not lessthan the peripheral length of the blank to be cut, carried thereby; incombination with a gear-blank carrier; means for moving one carriertransversely with relation to the other; and gearing connecting saidcarriers.

HERBERT WARREN.

Witnesses:

FRED. J. DoLE, EMORY (J; WHITNEY.

